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Research Papers: Hydrodynamic Lubrication

Effects of Shaft Shape Errors on the Dynamic Characteristics of a Rotor-Bearing System

[+] Author and Article Information
Fangxu Sun

National Key Laboratory of Science and Technology on Vessel Integrated Power System,
Naval University of Engineering,
Wuhan 430033, China
e-mail: sunfx2013@hotmail.com

Xianbiao Zhang

National Key Laboratory of Science and Technology on Vessel Integrated Power System,
Naval University of Engineering,
Wuhan 430033, China
e-mail: zxb1986@126.com

Xing Wang

National Key Laboratory of Science and Technology on Vessel Integrated Power System,
Naval University of Engineering,
Wuhan 430033, China
e-mail: xingwang.v@qq.com

Zhenzhong Su

National Key Laboratory of Science and Technology on Vessel Integrated Power System,
Naval University of Engineering,
Wuhan 430033, China
e-mail: suayst@163.com

Dong Wang

National Key Laboratory of Science and Technology on Vessel Integrated Power System,
Naval University of Engineering,
Wuhan 430033, China
e-mail: wangdongl@vip.sina.com

Contributed by the Tribology Division of ASME for publication in the Journal of Tribology. Manuscript received January 22, 2019; final manuscript received June 18, 2019; published online July 17, 2019. Assoc. Editor: Alan Palazzolo.

J. Tribol 141(10), 101701 (Jul 17, 2019) (9 pages) Paper No: TRIB-19-1033; doi: 10.1115/1.4044083 History: Received January 22, 2019; Accepted June 18, 2019

Effects of shaft shape errors are studied on dynamic characteristics of a rotor-bearing system. Stability characteristics of the cylindrical journal bearing are studied. It is shown that the rotating speed at which the oil whip occurs increases when the shape errors exit. And, there is a threshold speed of the bearing with shaft shape errors; before the speed is increased to the threshold, orbits of the center of the journal decrease, and when the speed exceeds the threshold, the orbits increase dramatically and oil whip appears. Furthermore, the quantitative relationship between shaft shape errors and bearing reaction forces of the rotor-bearing system is obtained, which is verified by experiments using rotors with different machining precisions. In order to reduce computing time, variational principle is applied when solving Reynolds’ equation.

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References

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Figures

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Fig. 1

Schematic diagram of the cylindrical journal bearing

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Fig. 2

Shaft shapes under different waviness order Nr: (a) Nr = 2, (b) Nr = 3, and (c) Nr = 4

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Fig. 3

Model of the rotor: (a) 3D model of the rotor and (b) simplified rotor model

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Fig. 4

Test rig of the rotor: (a) schematic diagram and (b) picture of the real test rig

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Fig. 5

Vertical displacement (x) according to the order of the shape errors

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Fig. 6

Orbits and the corresponded waterfall graph when Nr = 2, ANr = 0.06: (a) orbits, (b) orbits, and (c) waterfall graph

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Fig. 7

Bearing characteristics under different working conditions

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Fig. 8

Frequency spectrums of vertical bearing reaction forces of the first rotor by simulation: (a) front end, ANr = 0.06 (5000 rpm) and (b) back end, ANr = 0.06 (5000 rpm)

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Fig. 9

Frequency spectrums of vertical bearing reaction forces of the second rotor by simulation: (a) front end, ANr = 0.02 (5000 rpm) and (b) back end, ANr = 0.02 (5000 rpm)

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Fig. 10

Waterfall of vibration acceleration of bearing seats for the first rotor: (a) front end, ANr = 0.06 and (b) back end, ANr = 0.06

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Fig. 11

Waterfall of vibration acceleration of bearing seats for the second rotor: (a) front end, ANr = 0.02 and (b) back end, ANr = 0.02

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Fig. 12

Dimensionless vibration acceleration at 5000 rpm

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